Machine for milling, profiling, and the like



April 1936- L. F. NENNINGER El AL ,036,293

MACHINE FOR MILLING, PROFILING AND THE LIKE Filed May 31, 1935 7 Sheets-Sheet 1 mvamoa; 15m? [AF/mm;

ATTORNEY.

April 7, 1936. F. NENNINGER ET AL 2,036,293

MACHINE FOR MILLING, PROFILING AND THE LIKE Filed May 31, 1935 7 Sheets-Sheet 2 ATTORNEY.

April 7, 1936. L. F. NENNINGER ET AL 2,

MACHINE FOR MILLING, .PROFILING AND THE LIKE 7 Sheets-Sheet '5 Filed May 31, 1955 m 3% ma ATTORNEY.

April 7, 1936'. L. F. NENNINGER Er AL 2,036,293

MACHINE FOR MILLING, PROFILING AND THE LIKE 7 Sheets-Sheet 4 Filed May 31, 1935 an fl f f 2% 5% mflf w W 2 Z5 w? w r ATTORNEY.

A ril 7, 1936 F. NENNINGER ET AL 6- 93 MACHINE FOR MILLING, PROFILING AND I'HE LIKE Filed May 51, 1935 7 Sheets-Sheet 5 A TORNEY.

April7, 1936. 2,036,293

MACHINE FOR MILLING, .PROFILING AND THE LIKE L. F. N ENNINGER ETAL Filed ma 51, 1935 7 Sheets-Sheet 7 Ill 1 f w mm d M m 0 W? n 0 m A Z .5

Patented Apr." 7, 1936 UNITED STA ES 'roa MILIJNG, enormous,

-- mm on LIKE Lester F. Nenningcr, Millard Romaine, and

- nard Sassen, Cincinnati, 01110. more to The Cincinnati Milling Machine 00., @inc Ohio, a corporation of bills application y Ell, lath, d v

as c. (ill. tin

invention relates to machine tools and more particularly to an improved machine suitable for milling, profiling or the like.

One of the objects of this invention is to 5 provide a. power transmission and control mechanism for a machine oi the above character which is so contrived that part oi the power may be utilized during manual operation to reduce the edort of the operator and thereby maize in possible the easy manual maneuvering ol heavy slides ior pro ,1 r r, operations.

another object oi this invention is to so con trim a power transmission and control mechanism ior edecting power'ieeding movements 15 between the tool andworlr oi a milling cethat a fractional horse power prime mover may be utilized to edect, control, and regain c said movement.

it further object oi this invention is to provide at each movable slide oil a machine oi the character described with an individual power imit at e servo-type which may be utilised at all too tor adjustment thereof, regardless oi whether said adjustment is ellccted manually or by tit power.

rm additional object of this invention is to facilitate manual adjustment or the various slides of a milling machine whereby each slide, may

l be easily and quickly manually adjusted with i the same minimum of short, regardless oi the weight of the slide or the direction inwhich it is moved, thereby making it possible to build large heavy profiling machines tor manual operation. V

1% A still further object oi this invention is to provide a centralized manual control station irom which the movement oi all slides may be conveniently governed so as to render the machine suitable tor profiling purposes.

Other objects and advantages ol' the present invention should be readily apparent by referonce to the following specification, considered in co'niunction with the accompanying drawings forming a part thereof and it is to be underit stood that any modifications may be made in the enact structural details there shown and described, within the scope of the appended claims,

without departing from or exceeding'the spirit oi the invention. so Referring to the drawings in which like reference numerals indicate like or similar parts:

Figure l is an elevation of an exemplary emboent of this invention.

Figure 2 is a view of the machine shown in Figure l as viewed from the right of that figure.

' mechr Fe fl is a rear view oi the achine own in. t L i 5E 1-; r

Fagin-e t is a detail view ol'the saddle operating puma as view on the e i-t oi Figure it Fe t is a section on the c 5-5 oi msure 2.

Figure 6 iso section on the line t-t oi Figuret.

Fie "l is a section on the e ll oi gm I are i.

Fin n is a section on the line at Fig um i.

Fie o is a schetic diagram oi the t c mission and control mechanism oi the hence. it

Figure in is a mood i'orm oi trassion and control circuit tor the mace.

Figure ii is a detail view oil a hydraulic ra control device.

Figure 1a is a dlagraatic view oi an elec go trlcal rate control device.

Figure it is a diagrammatic view of a mechanical rate control device. Figures it and iii are views representing dii i'erent dial systems utilized iorindicating the as length oi slide movement.

There is shown in Figures 11, 2 and 3 oi the drawings an exemplary embodiment of the machine and it will be noted that the machine has three relatively movable slides, til, it and it, it Since it is conventional practice, however, to distinguish oridentily the slides by the elements carried thereby, this will be done, although the terms so applied are not to he considered as itlng. V I For instance, the slide it may he termed the worlr supporting slide or the worlr table; the slide llli may be termed a saddle and the slide lid ' it may be termed the tool support or spindle carrier. The various elements may be will at tributed as respects the several slides, but in any event the final purpose is to obtain three-direc- "tlonal relative movement betweenthe tool and feasible, the expedient of mechanical advantage 65 was resorted to, but since there is a practical limit to the'amount of mechanical advantage that can be applied, it has required a great amount of exertion on the part of the operator to move heavy slides, resulting in the fact that it was highly impractical for the operator to attempt to maneuver the tool through an irregular cutting path usually required in profiling operations.

In addition, the mechanism for producing power movement at variable rates required heavy and cumbersome gear boxes, which represent a large investment in parts, some of which are perhaps never used, or at the best, utilized very little.

In conventional hydraulically operated milling machines no provision has been made for manually eilecting relative movement between the tool and work with the result that manual guided profiling operations are impossible on such machines.

The transmission and control mechanism of the present machine is designed to eliminate these various difiiculties and to provide a machine in which the various slides may be freely and easily moved by hand, with practically no efiort regardless of their resistance against movement whereby the tool may be easily manipulated along an irregular cutting path as required in profiling operations; or fed by power at controlled variable rates with a mechanism which is very light, compact and composed of a relatively small number of parts.

In other words, the present invention contemplates the use of a power unit; of a servo type for the individual slides, together with suitable manual and power operable means for selectively controlling operation of said unit, with the result that; the controlling force to be applied is the same in all cases regardless of whether it is applied by hand, or by power; and regardless of the final load or resistance to\be overcome. This force is so small that two slides can be simultaneously controlled by the operator in a very easy and convenient manner, whereby exceptionaly large machines of the character disclosed may be built and utilized for hand controlled profiling operations, which otherwise would be impracticable and almost impossible.

The table I0 is provided with a cylinder I3 which is .fastened to the underside of the slide as more particularly shown in Figure 2, the cylinderhaving a contained piston M which is operatively connected by a piston rod l5 to a bracket l6 which is fixed to the bed I! of the machine. The table I 0 is supported in guide ways l8 formed in the bed and this movement is efiected by admitting pressure fluid to one end or the other of cylinder l3.

The saddle II is also provided with a cylinder l9 which 'is attached to the underside thereof, as more particularly shown in Figure 3. This cylinder has a piston 20 which is operatively connected by a piston rod 2| to a bracket 22 which is fixed to the bed of the machine. The saddle is supported on guide ways 23 and is moved therealong by admitting pressure fluid to one end or the other of cylinder 20.

Likewise the vertical slide or spindle carrier l2 has a cylinder 24 secured to one side thereof as more particularly shown in Figure 1 and this cylinder has a contained piston 25 operatively connected by a piston rod 26 to a fixed bracket 21. The slide [2 is vertically movable by admitting pressure to one end' or the other of cylinder 24 along the vertical guide ways 28 formed on one vertical face of the saddle H.

The servo unit which ultimately controls the admission of fluid pressure to the opposite ends of a slide cylinder is the same for each slide and therefore only one of these units will be explained, and that one will be the unit connected for control of the slide l2 and which is shown in detail in Figure 5.

The opposite ends of cylinder 24 are connected by pipes 29 and 30, which are connected to ports 3| and 32 of a valve member 33 which is fixed with the bracket 34 carried by the slide l2 and movable therewith, as shown in Figure 7. These ports intersect longitudinal bores 35 and 36 respectively which terminate in annular grooves 31 and 38 formed in the periphery of the valve member 33. Additionally, the member 33 has a central or axial bore 39 which is connected by a channel 40 to a source of fluid pressure. The bore 39 interconnects a diametrical bore 4|, the opposite ends of which terminate inthe periphery of the member 33 and opposite a pair of arcuate slots 42 and 43 cut in the periphery of the sleeve 44.

It will be noted that the annular grooves 31 and 38 form an intermediate spool 45, whereby when the parts are in the position shown in Figure 5 the pressure fluid from the supply pipe 40 will pass in suitable proportions to the annular grooves and thereby through the pipes 29 and 30 to opposite ends of the cylinder to create equal resultant opposing pressures on the piston, in spite of its dififerential areas, and thereby hold the slide against movement.

The sleeve 44 is provided with an additional pair of diametrically opposite arcuate grooves 46 and 41 spaced to one side of the arcuate grooves 42 and 43 and with a second pafir of diametrically oppositaarcuate grooves 48 and 49 spaced on the opposite side of the grooves 42 and 43. The grooves 46, 41, 48 and 49 are exhaust grooves and are so positioned that when the parts are in the position shown in Figure I 5, neither one of the annular grooves 31 and 38' are connected thereto, but upon the slightest relative movement between the member 44 and the member 33, one of these grooves will be connected to exhaust, whereby movement; of the slide 24 will be eifected.

It will be noted that the member 44 has a reduced portion around which is fitted an outer sleeve 50 in which is formed radial holes 5! opposite the grooves 46, 41, 48 and 49 through which the exhaust fluid may escape.

The member 44 is freely slideable relative to the member 33 upon which it is guided, but it is held against axial movement by a threaded quadrant 52 which, as shown in Figure 6, is held in engagement with the screw 53 by the spring pressed ball 54. From the construction, as shown in Figure 6, it will be seen that the member 44 is held against rotation.

The screw 53 is keyed or otherwise secured to the shaft 55 which is anchored against longitudinal movement by a thrust bearing 56, which is interposed between the end of the screw 53 and the upper end of the tubular housing 51 which is attached or otherwise secured as by bolts 58 to the saddle II.

The shaft 55 extends downward through the tubular housing 51 into the gear box 59 in which is rotatably supported a pair of bevel gears 60 and GI co-axial of the shaft 55 and intermeshing with a common bevel gear 62. The bevel slide 24.

thereof adapted to selectively interengage clutch teeth 66 or ,8! formed on the opposing faces of gears 60 and 6| respectively. Thus, by shift-" ing the clutch from the neutral position shown the shaft 55 may be rotated by power and thereby through the screw 53 and nut segment 52 a the sleeve 44 may be moved relative to the valve member 33 to connect pressure to one end of cylinder 24 and connect the other end of the cylinder to exhaust to cause movement of the The movement of the slide will, in turn, through the bracket 3i attached thereto, cause movement of the member 33 in the same L direction as the sleeve 44 was moved and return the parts to the position-as shown in Figure 5,

thus stopping the slide movement.

Due to the length of the shaft 55 it was deemed advisable to support the upper end thereof, and

to this end a piston member 65 isv attached and IEO held thereto by a nut 69 threaded on the end ,of the shaft. This piston member slides in a bore Ill formed in a part of the irregularshaped housing 34.

To facilitate lubrication of the parts the fluidexhausting through the openings 5| is held in the interior of the housing 34 by a suitable gasket or seal II which slides along the exterior of the tubular housing 51. When the space in this housing becomes filled, the oil can escape through the radial passages 12 and axialbore I3, which -are adjacent the upper end of shaft 55, into thevupper end of the cylinder III, thereby lubricating the walls of the cylinder for easy movement of the piston therein, and any excess can overflow through the passage I4 into the chamber I5 and thereby. through the return pipe it into the gear box 59. This will lubricate the gears in the box and the excess fluid can return through the pipe 11 to reservoir.

The shaft 55 is provided with a bevel gear l8 on the lower end thereof, which'bevel gear may be connected through suitable means for manual operation of the shaft 55 when the clutch member 54 is in a central position. From the foregoing it will now be seen that a servo power unithas been provided for a slide which may be operated through manual means or by power means, and in either direction to effect opposite movements of the slide. This entire mechanism, as shown in Figure 5, is duplicated for each of the other movable slides of themachine and for purposes of identification the servo motor unit for the slide I is indicated generally by the reference,numeral I9 in Figure 9 and the servo motor unit for the'slide H is indicated generally by the reference numeral .80.

Referring to Figure 9, these units derive their pressure from an accumulator M which. in turn, 4

is supplied by a pump 82. The accumulator 8i has a main delivery channel 83 which is connected to a header 84 and from this header there is a channel 40 extending tog-the servo motor unit for the vertical slide; a channel 85 which supplies pressure to the servo unit 80 for the saddle, and a channel 86 which supplies fluid pressure to the servo unit I9 of the table II).

The pump 82 has an intake 81 through which it draws fluid from a reservoir 88 located in, a suitable position in the bed of the machine and the accumulator 8 I.

a delivery port 89 to which is connected a channel 90 that carriers the fluid under pressure to The channel 90 may have a relief valve 9| connected thereto for safety purposes. The use of the accumulator makes it possible to have large quantities offluid under pressure available for immediate use.

The pump 82 has connected to it a shaft 92 I2 of the machine. This transmission is'a variable speed mechanism and comprises a first shaft I 03 which is connected through gearing M4 to shaft I05 upon which is splined the clutch memher 605 for connecting the shaft to the constantly driven clutch member Mill. The clutch I05 is shifted by the shifter fork )8 which is centrally pivoted at I09 and connected'by a link III] to a crank III, which, as shown in Figure 2, is secured to a shaft [H2 having a manually operable lever II3. This lever, it will be noted, is adjacent the front of the machine for easy access by the operator.

The shaft M3 has a first pair of shiftable gears lid and a second pair of shiftable gears II5 splined thereon for selective interconnection with gears H6, li'I, M8 and M9 carried by shaft i20, whereby this shaft may be rotated at four difierent speeds. The shaft I also has a shiftable gear lZI which may be directly connected to gear i122 for effecting one direction of rotation of the spindle, or indirectly by engagement with gear I23 and the co-axial idler I24,for

rotation of the spindle in an opposite direction. The gear I22 intermeshes with a gear I25 which is splined on a shaft I26, the gear I25 being, held aga nst longitudinal movement in" thebracket I2'l mounted on the bedof the machine, and the shaft i28 being fixed in the bracket m, fixed for movement with the saddle ii. The

bracket I28 has a pair of bevel gears M9 and I30 joumaleol therein, one of them being fixed upon upward or downward movement of the slide the shaft will slide through the bevel gear I30. The shaft MI is connected through bevel gearing I32 and spur gear I33 to the tool spindle I02. Thus, by means of the sliding joint in g the bracket i128 and the sliding joint in the bracket I21 the spindle may be moved in two directions while still being rotated by the prime mover IOI located in the bed of the machine.

The shiftable gears fi l and H5 constitute a speed change mechanism for thetool spindle and these are shifted by levers mounted on the outside of the gear box I34, as more'particularly shown in Figure 2. The lever I85 is integrally connected to a shaft I36 to which is connected an arm I31 having a shifter fork I38 pivotally connected thereto and engaging the gear couplet Ill. The lever I is shiftable against the stop I40 to engage one gear of the couplet with gear IIIi and against-the stop III to engage the other gear of the couplet Ilt with gear Ill and to a third or central position, such as that shown in Figure 2, to disengage the couplet from both gears H6 and H1.

The lever I42 is integrally connected to a shaft I43 which has an arm I44 fixed therewith inside of the gear box which pivotaliy supports a shifter fork I45 for shifting the couplet II5. When the lever I42 is moved against the stop I46, one gear of couplet II engages the gear H8 and when the lever is shifted against the stop I41 the other gear of the couplet is intermeshed with gear H9. The lever I42 also has a third position which, as shown in Figure 2, disengages the couplet from both gears H8 and H9. This mechanism constitutes a speed changemechanism for varying the speed of rotation of the tool spindle.

There has been nested in a convenient position at the front of the machine a group of control levers for determining manual operation of the various slides whereby the operator may simultaneously control the movement of any two slides without changing his position. This group of controls is shown in Figure 1 and comprises the rotatable hand wheel I52 which may be utilized to control vertical movement of the car.- rier I2; a hand wheel I53 which is operatively connected for controlling movement of the saddle II and a hand wheel I54 which is operatively connected for controlling movement of the table Ill.

As shown in Figures 2 and 9, the wheel I52 is fixed to the end of l shaft I55 which is fixed against axial movement in the bed I1 and extends through the saddle into the splined connection with a bevel gear I56 which is fixed for movement with the saddle. This shaft has a dial I51 integral therewith adjacent the hand wheel I52 which cooperates with the fixed pointer I58 for indicating the amount of adjustment effected. This dial may be graduated in thousandths of an inch and the number of such graduations may depend upon the amount of movement to be eflected for one rotation of the hand wheel. As shown in Figure 14, if one rotation of the hand wheel effects one-tenth of an inch slide movement, the dial may be subdivided into one hundred'gra'duations. and a linear scale I59 graduated in tenths .of an inch and coopcrating with the rotatable dial to indicate the total movement effected.

On the other hand, as shown in Figure 15, if one rotation of the hand wheel effects a A" movement, the dial I51 may be divided into 250 graduations and the linear scale I59, utilized therewith, divided into quarters of an inch. The linear scale, such as I59, may be attached to the column I I and the pointer I68 attached to the carrier, whereby relative movement may take place between the parts. Since the scale I59 is positioned for observation from the front of the machine the operator may very easily compute from that scale and from the dial I51 the length of any desired movement he wishes to make.

Since it may be desirable at this time to control the machine from the rear side of the table I6, as viewed in Figure 1, an additional hand wheel "I may be provided and operatively connected, as shown in Figure 3, by a sprocket and chain connection indicated generally by the reference numeral I62 to the shaft I55. This hand wheel ay also have a dial I63 integral therewith; J1

Theh'and wheel I53 is operatively connected by a sprocket and chain, indicated generally by the reference numeral I64, to shaft I65 which corresponds to an extension of shaft 55' shown in Figure 5. This will control operation of the servo unit 88 and thereby in and out movement of the saddle II.

The bevel gear 18 of the unit 80 may be connected to a bevel gear I66 and to a second hand wheel I61, which as shown in Figure 4, permits adjustment of the saddle from a position adjacent the end of the table ID.

The hand wheel I54 is operatively connected by a chain and sprocket connection indicated generally by the numeral I68 to shaft I69, which shaft is connected by a bevel gear I to the bevel gear 18 of the servo motor unit 19. This shaft extends beyond the rear of the bed I1, as shown in Figure 3, where it is provided with a second hand wheel I1I whereby movement of the table I0 may be controlled from either side of the bed I1.

As shown in Figure 1, the table I0 may be provided with a pointer I12 cooperating with a linear scale I13 which is fixed with the bed for indicating the amount of slide movement. Similarly, as shown in Figure 2, the saddle may be provided with a pointer I14 movable therewith with respect to a fixed scale I15.

As previously mentioned in connection with Figure 5, each servo unit has a power shaft 63 whereby movement of the slide may be power effected, and by means of the mechanism now to be described, this movement may be effected at variable feed rates and an adjustable dog rip mechanism is also provided for terminating the power movement at desirable points.

Since the actual power necessary to rotate the shaft 63 of any one of the servo units is only a fraction of one horse power, the power operable means for rotating it may be very light, compact and inexpensive to manufacture. In Figure 9, there is shown one form of variable feed mechanism, and since this mechanism is the same for each of the three slides only one will be described in detail. Taking the vertical carrier I2 as an example, the shaft 63 has connected to it a fluid operable motor I16. This motor is supplied with fluid pressure from the accumulator 8I, which has a second supply pipe I11 connected to a header I18 from which extends three branch lines I19, I83 and I8I for supplying fluid to the motors of the three slides. As shown in Figure 9, the line I80 'i's'connected to a feed rate control mechanism, indicated generally by the reference numeral I82. This mechanism actually comprises a throttle device which is shown in detail in Figure 11. The shaft I83 to which is connected the handle I84 has a cam I85 keyed therewith for controlling the position of a spring pressed throttle I88. The line I88 is connected to a port' I81 in the valve sleeve I88 and the plunger I86 has a tapered spool I89 which determines the drop ifispressure to port I90 and thereby to the motor The spring I9I tends to shift the plunger I 88 in a direction tending to open port I98 and the cam has a configuration, which upon rotation thereof in a counterclockwise direction, will gradually close the port I90. A suitablegraduated dial I92 may be keyed with the/shaft I83 for indicating the various feed rates effected.

A similar throttle mechanism, indicated generally by the reference numerals I93 and I94, may be provided on the front of the machine and suitably connected for controlling the rate be fixed against axial movement in the bed II. This sleeve may have a spline connection with the spline shaft 211 which is operatively connected to the bevel gear 62 in the reverser box for the slide l2. The shaft 211 is fixed for movement with the saddle and the spline connection between it and the sleeve 216 permits this movement while maintaining a driving connection to the bevel gear 62.

There has thus been provided an improved transmission and control mechanism for milling machines which permits of easy and quick manual adjustment of any of the slides thereof, regardless of their actual resistance against movement, and in which the various slides may be moved by a power operable mechanism which is variable as to rate but which is simple, compact and inexpensive to manufacture.

We claim:

1. In a machine tool having a work carrier and a tool carrier, the combination of means for effecting relative movement between the carriers comprising an hydraulic servo-motor mechanism having a control valve consisting of two relatively movable members, one of which is attached to the movable carrier, manual means for moving the other member of said valve to cause actuation of the servo-motor and thereby relative movement between the carriers, a power operable member, and means for selectively coupling said member for also causing movement of said other member.

2. In a machine tool having a work carrier and a tool carrier, the combination of means for effecting relative movement between the carriers comprising a servo-motor mechanism having a fluid operable part permanently connected to one of said carriers, a servo-valve having relatively movable valve members for determining the direction of application of pressure to said member and thereby the direction of said relative movement, manually operable means for relatively shifting said valve members whereby relative movement between the carriers may be controlled at will, and. power operable uniformly actuated means selectively connectible for effecting a uniform continuous movement of one of said valve members and thereby a uniform rate of relative movement between the carriers.

3. In a machine tool having a work carrier and a tool carrier, the combination of fluid op erable means for effecting relative movement between the carriers includinga servo-valve, a screw operatively connected for actuation of said valve, and power operable means for causing uniform rotation of the screw and thereby a uniform relative feeding movement between the carriers.

4. In a machine tool having a work carrier and a. tool carrier, the combination of fluid operabl'e means for effecting relative movement between the carriers including a servo-valve, a screw operatively connected for actuation of said valve, power operable means for causing uniform rotation of the screw and thereby -a uniform relative feeding movement between the carriers, trip dogs carried by the movable carrier, and means actuable thereby for interrupting'movement of the servo-valve by said power means.

5. In a machine tool having a cutter support and a work support, the combination of a servomotor, said motor consisting of relatively movable parts, one of which is attached to one of said supports, a servo-valve comprising two relamotor having relatively sures 01 said motor will tively movable valve parts, one of which is connected to the movable support, a screw anchored against axial movement, a nut segment carried 1 by the remaining valve part and engaging said screw, and means to actuate said screw to effect relative movement between the supports.

6. In a milling machine having a bed, a work table reciprocably mounted upon the bed, and a tool spindle supported in adjacent relation to the table, the combination of means for effecting translation of the table relative to the spindle comprising a fluid operable servo-motor having a differential piston operatively connected to the table, a servo-control valve having a pressure port and a pair of delivery ports for delivering fluid to opposite ends of said piston, a valve spool eccentrically positionable with respect to said pressure port to prevent movement of said table, and means for shifting said spool in opposite directions with respect to said eccentric position to effect opposite movements of the table.

7. In a machine tool having a work carrier, a tool carrier, and a tool spindle journaled in the last named carrier, of means for moving said work carrier transversely to the axis of said spindle including an hydraulic servo-motor having a servo-control valve, a rotatable screw for shifting said servo-valve, manually operable means permanently operatively connected to the screw for effecting actuation thereof, a source of power, and a control clutch for selectively connecting said power means for actuation of the screw to effect uniform feeding movement of the work carrier.

8. In a machine tool having a bed, a work table reciprocably mounted upon said bed, and a tool carrier supported for movement in a plane normal to the axis of table movement, the combination of a fluid operable motor for shifting one of said parts, a servo-control valve for said motor having relatively movable control elements, one of which is fixed for movement with said movable part, and the other element held for independent movement with respect to said moving part, said last named element having a predetermined position with respect to its cooperating element whereby the resultant pressures of said motor will be equalized, manually operable means on the side of the bed opposite to the.-

member for opposite actuation of said other element and thereby a relative movement at a uniform rate and in accordance with the rate of actuation of said power operable member.

9. In a machine tool having a.bed, a work table reciprocably mounted upon said bed, and a tool carrier supported for movement in a plane normal tothe axis of table movement, the combination-of a fluid operable motor for shifting one of said parts, a servo-control valve for said movable control elements, one of which is fixed for movement with said movable part, and the other element held for independent movement with respect to said moving part, said last named element having a predetermined position with respect to its cooperating element whereby the resultant presbe equalized, manually side of the bed opposite the tool carrier is supoperable means on the to the side at which horse power motor adapted to be operatively connected for rotation of said screw, and means to vary the rate of rotation of said screw by said motor.

19. A profiling machine comprising a bed, a

work table reciprocably mounted upon the bed,

a piston and cylinder, one of which is supported by the bed and the other operatively connected to the table for eifecting actuation thereof, a first slide supported by the bed for movement toward and from the table, a second slide supported by said first slide for movement in a direction normal to the direction of movement of the fizst slide, a pair of fluid operable motors respectively connected for moving said slides, a pump for supplying fluid under pressure to said motors and to said cylinder, a cutter spindle iournaled in one of said slides, a prime mover mounted in the bed of the machine, a variable speed transmission operatively connected for actuation ofthe spindle, a control clutch for selectively connecting said transmission to the primemover, means for connecting the'pump to the prime mover for continuous actuation thereby, individual servo-control valves interposed between the pump and each of said motors and cylinder, said servo-control valves being located adjacent the slides which they control, and remote manually operable means for each of said servo-control valves clustered at an operating station at the front of a machine whereby the operator may quickly and effortlessly control the relative movement between the tool' spindle and the work table in three directions.

20. A profiling machine comprising a bed, a work table reciprocably mounted upon the bed, a piston and cylinder, one of which is supported by the bed and the other operatively connected to the table for effecting actuation thereof, a first slide supported by the bed for movement toward and from the table, a second slide supported by, said first slide for movement in a direction normal to the direction of movement of the first slide, a pair of fluid operable motors respectively connected for moving said slides, a pump for supplying fluid under pressure to said motors and to said cylinder, a cutter spindle iournaled in one of said slides, a prime mover mounted in the bed of the machine, a-variable speed transmission operatively connected for actuation of the spindle, a control clutch for selectively connecting said transmission to the prime mover, means forconnecting the pump.

to the prime mover for continuous actuation thereby, individual servo-control valves interposed-between the pump and each of said motors and cylinder, said servo-control valves being located adjacent the slides which they control, .remote manually operable means for each 01' said servo-control valves clustered at an operating station at the front of a machine whereby the operator may quickly and eflortlessly control the relative movement between the tool spindle and the work table in three directions, individual fractional horse power motors for actuation of the respective screws, and means clustered with said manual control means for controlling the connection of the motors to the respective screws.

21. A profiling machine comprising a bed, a work table reciprocably mounted upon the bed, a piston and cylinder, one of which is supported by the bed and the other operatively connected to the table for effecting actuation thereof, a first slide supported by the bed for movement toward and from the table, a second slide supported by said first slide 'for movement in a direction normal to the'direction of movement of the first slide, a pair of fluid operable motors respectively connected for moving said slides, a pump for supplying fluid under pressure to said motors and to said cylinder, a cutter spindle joumaled in one of said slides, a prime mover mounted in the bed of the machine, a variable speed transmission operatively connected for actuation of the spindle, a control clutch for selectively connecting said transmission to the prime mover, means for connecting the pump to the prime mover for continuous actuation thereby, individual servo-control valves interposed between the pump and each of said motors and cylinder, said servo-control valves being located adjacent the slides which they control, remote manually operable means for each of, said servo-control valves clustered at an operating station at the front of a machine whereby the operator may quickly and effortlessly control the relative movement between the tool spindle and the work table in three directions, individual fractional horse power motors for actuation of the respective screws, means clustered with said manual control means for controlling the connection of the motors to the respective screws,

and trip operable means associated with each slide for terminating power movement thereof.

22. In a milling machine having a plurality 'for selectively connecting said shaft with each of said screws for power actuation thereby.

LESTER F. NENNINGER. LULLARD ROMADIE. BERNARD SASSEN. 

